|Publication number||US2214057 A|
|Publication date||Sep 10, 1940|
|Filing date||Nov 27, 1936|
|Priority date||Dec 24, 1934|
|Publication number||US 2214057 A, US 2214057A, US-A-2214057, US2214057 A, US2214057A|
|Inventors||Harry B Hull|
|Original Assignee||Gen Motors Corp|
|Export Citation||BiBTeX, EndNote, RefMan|
|Referenced by (12), Classifications (17)|
|External Links: USPTO, USPTO Assignment, Espacenet|
Sept. 10, 1940. H, H 2,214,057
7 REFRIGERATING APPARATUS Original Filed Dec. 24, 1934 2&5 an,
319 an an (n I 3:0 '65, INVENTOR. 1, BY & .M,MMZMU l/l's ATTORNEYS Patented Sept. 10, 1940 UNITED STATES PATENT OFFICE REFRIGERATING APPARATUS Harry B. Hull, Dayton, Ohio, assignor to General Motors Corporation, Dayton, Ohio, a corporation of Delaware 4 Claims.
1rThis invention relates to the conditioning of a It is an object of this invention to provide a novel heat exchange unit which is especially adaptablefor use in air conditioning apparatus,
which are capable of dehumidifying the air with substantially no reduction in dry bulb temperature when conditions require such treatment and which are capable of conditioning the air with a reduction of dry bulb temperature in varying amounts as conditions require.
It is another object of this invention to provide a heat exchange unit which may be used for conditioning a plurality of streams of fluid.
Still another object of this invention is to provide a head exchange unit which is of light weight, inexpensive, and at the same time, rugged and efficient.
Further objects and advantages of the present invention will be apparent from the following description, reference being had to the accompanying drawing, wherein a preferred form of the present invention is clearly shown.
In the drawing:
5 Fig. 1- is a view, somewhat diagrammatic, and
partly in cross-section of an apparatus embodying features of my invention; and
Fig. 2 is a view in perspective of a portion of the apparatus shown in Fig. 1.
30 My novel heat exchange unit is especially suitable for use in apparatus of the type shown in Fig. 1 of the drawing. In the apparatus shown in the drawing, air may enter through the inlet 300 from the space 30| or from outside space, or
35 from both. It may flow under action of a blower 302 driven by motor 303 either into the passageway 304 or passageway 305, or both. If it flows through the passageway 304, it comes into thermal exchange relationship with the evaporator 308 by passing through the passages 309 formed by the corrugated metal sheet 310 which is placed inside of the metal box 3 the sides of which come incontact with the coils 3|2 of the evaporator 308. After passing through the passage- 5 ways 309, the air is discharged through the passageway 3I3, and through outlet 3l4, into the space 30 I.
.If the damper 3|5 swings to the left, then the air from blower 302 flows into passageway 305,
50 from whence it comes in thermal exchange with the secondary refrigerant evaporator 3I6 thence in thermal exchange with the evaporator 308 thence in thermal exchange with the secondary refrigerant condenser 3ll. Thereafter the air 5 is discharged through the outlet 3! into the space 30l. Under such conditions the air flowing in thermal exchange with the evaporator 308 passes through vertical passageways 319 formed by the corrugated metal sheet 320 placed in contact with the coils 3l2 of the evaporator 308. t 5 The flow of air through the apparatus, and consequently the amount of heat which is transferred to the secondary refrigerant, is governed in accordance with air conditions, preferably the relative humidity conditions of the air in space 10 Thus the psychrometer 32! actuates the lever 322 which in turn actuates the rod 323 which is connected to the damper M5 and switches it about the fulcrum 324. The psychrometer 32l may include a dry bulb 325 and a wet bulb 325 15 in opposed relationship. The construction is such that as relative humidity rises, the pressures in the bulbs 325 and 326 tend to equalize, and under such conditions the damper 3 I 5 is swung upwardly toward the left causing the flow through pas- 20 sageway 305 in thermal exchange with the evaporators 3 I 6, 308 and with the condenser 3 I 1. When the relative humidity is low, then the tendency of the flow of air is through the passageway 304. A spring 321 opposes slightly the thrust of dry bulb 325 and its tension may be adjusted by the screw and knob 328 so that the relative humidity to which the psychrometer is responsive may be varied for individual requirements.
It is to be understood that, with respect to Fig. 1 the position of the air dampers may be intermediate, so that part of the air may be flow ing in thermal contact with the secondary refrigerant while part of the air does not come in thermal contact with the secondary refrigerant. Thus the action described may vary from one extreme to the other and to any intermediate position.
The primary evaporator 308 may be connected to a refrigerant liquefying unit 321a. This unit v may include a motor 328a, compressor 329, primary refrigerant condenser 330, and liquid receiver 33!. Liquid primary refrigerant flows through the line 332 through valve 333, which automatically introduces liquid refrigerant into the evaporator 308 when the pressure in the evaporator is reduced below a predetermined limit, into the lower header 334. From thence the refrigerant flows in parallel relationship through a plurality of sinuous conduits 3l2 to'the upper 0 header 335. From thence the evaporated refrigerant returns through the line 336 through the compressor 329. The valve 333 may be provided with a thermostatic bulb 331 placed in thermal exchange with the outlet of the evaporator and which automatically throttles the valve 333 when the refrigerant efiect becomes suiflciently efiective on the bulb 331. The calibration of the valve 333 preferably is such that the temperature of the air cooling surface of the evaporator 308 is maintained above the freezing point of water, but it is to be understood that, if desired, the evaporator may be operated at any temperature below the freezing point of water and may be periodically defrosted either during each cycle of the unit or by a special defrosting cycle.
The cooling action of the primary refrigerant may be controlled by starting and stopping the liquefying unit 321a. Thus, the motor 328a may be started and stopped by the switches 338 and 339 placed in electrical parallel relationship and which are actuated by dry bulb 348 and wet bulb 3 respectively. A hand switch 342 may be provided in such a position that the motor 303 must be first operated before the motor 328a can be operated. If desired, the switches 338 and 339 may be replaced by a psychrometer of the type shown in Fig. 7 of my parent application, Serial No. 758,884, now Patent No. 2,093,725 issued September 21, 1937, of which this is a division, or the switches 338 and 339 may be replaced by a switch similar to the switch .40 shown in Fig. 1 of the above mentioned application, in which case the operation of the unit 3210. will be in response to the efiective temperature in space 30 I.
While the preferred form of automatic controls have been specifically illustrated and described, it is to be understood that their form and character may be modified, if desired. For example, wherever a dry bulb thermostat is illustrated or described, the same may be replaced by a Wet bulb thermostat, humidostat or effective temperature responsive instrument. Likewise wherever a wet bulb thermostat, humidostat or effective temperature responsive instrument is illustrated or described, the same may be replaced by any one of the other three controls referred to.
While the form of embodiment of the present invention as herein disclosed, constitutes a preferred form, it is to be understood that other forms might be adopted, all coming within the scope of the claims which follow.
What is claimed is as follows:
1. In combination, an air temperature modifier having a plurality of sections of conduit through which an attemporating fluid is adapted to flow, corrugated metal sheets for spacing said sections, and a wall member between adjacent corrugated sheets separating the air flowing over one corrugatedsheet from the air flowing over an adjacent corrugated sheet, the corrugations of one of said sheets being arranged at an angle to the corru gations of another of said sheets whereby the air flowing over one of said sheets flows at an angle to the air flowing over another of said sheets, and means for varying the amount of air flowing over one of said sheets.
2. In an evaporator, means forming a refrigerant flow passage, means for directing one stream of air substantially vertically, and for directing another stream of air substantially horizontally in thermal exchange relationship with said refrigerant flow passage means, said air directing means comprising corrugated sheet metal members in thermal exchange relationship with said refrigerant flow passage means.
3. In combination, a coiled heat exchange ele-. ment, corrugated sheet metal means for direct-- ing a first stream of air substantially vertically in thermal exchange relationship with said element, corrugated sheet metal means for simultaneously directing a second stream of air substantially horizontally in thermal exchange relationship with said element, and means for varying the amount of air flowing in thermal exchange relationship with said element inone of said directions.
4. In combination, an air temperature modifier having a plurality of sections of conduit through which an attemperating fluid is adapted to flow, corrugated metal sheets for spacing said sections, and a wall member between adjacent corrugated sheets separating the air flowing over one corrugated sheet from the air flowing over an one of said sheets being arranged at an angle to the corrugations of another of said sheets whereby the air flowing over one of said sheets flows at an angle to the air flowing over another of said sheets, means for directing one stream of air over one of said sheets, andmeans for directing a separate stream of air over another of said sheets.
, HARRY B. HULL.
adjacent corrugated sheet, the corrugations of 4
|Citing Patent||Filing date||Publication date||Applicant||Title|
|US2885867 *||Apr 2, 1956||May 12, 1959||Mcfarlan Alden I||Air conditioning system and control|
|US3963466 *||Feb 18, 1975||Jun 15, 1976||Hynes William M||Compressed gas drying apparatus|
|US4501321 *||Nov 10, 1982||Feb 26, 1985||Blackstone Corporation||After cooler, charge air cooler and turbulator assemblies and methods of making the same|
|US4657070 *||Feb 15, 1984||Apr 14, 1987||Hudson Products Corporation||Air-cooled vapor condensers|
|US4735054 *||Aug 13, 1987||Apr 5, 1988||Honeywell Inc.||Method for minimizing off cycle losses of a refrigeration system during a cooling mode of operation and an apparatus using the method|
|US4966230 *||Jan 13, 1989||Oct 30, 1990||Modine Manufacturing Co.||Serpentine fin, round tube heat exchanger|
|US5725047 *||Jan 13, 1995||Mar 10, 1998||Lytron Incorporated||Heat exchanger|
|US6131653 *||Mar 8, 1996||Oct 17, 2000||Larsson; Donald E.||Method and apparatus for dehumidifying and conditioning air|
|US8069905 *||Jun 9, 2004||Dec 6, 2011||Usui Kokusai Sangyo Kaisha Limited||EGR gas cooling device|
|US20050098307 *||Jun 9, 2004||May 12, 2005||Usui Kokusai Sangyo Kaisha Limited||Gas cooling device|
|US20150198385 *||Jan 13, 2014||Jul 16, 2015||Deere & Company||Cross Flow Heat Exchanger|
|US20160161189 *||Dec 4, 2014||Jun 9, 2016||Honeywell International Inc.||Plate-fin tubular hybrid heat exchanger design for an air and fuel cooled air cooler|
|U.S. Classification||165/97, 62/180, 62/426, 62/176.5, 165/104.21, 62/186, 236/44.00R, 62/90, 165/152, 165/124|
|International Classification||F24F12/00, F24F3/14|
|Cooperative Classification||F24F3/1405, Y02B30/16, F24F12/001|
|European Classification||F24F12/00B, F24F3/14A|